Tank washing apparatus



Dec. 15, 1959 v. LIONE 2,917,243

TANK WASHING APPARATUS Filed Aug. 5, 1957 4 Sheets-Sheet 1 FIG.- 1

Leonard V. Lione Inventor By yw Attorney Dec. 15, 1959 L. v. LIONE2,917,243

TANK WASHING APPARATUS Filed Aug. 5, 1957 4 Sheets-Sheet 2 FIG.'6

Leonard V. Lione Inventor By /67 Attorney Dec. 15, 1959 v, LIQNE2,917,243

TANK WASHING APPARATUS Filed Aug. 5, 1957 4 Sheets-Sheet 3 lOlc lOlbLeohqrd V. Lione Inventor Dec. 15, 1959 Filed Aug. 5, 1957 L. v. LIONE2,917,243

TANK WASHING APPARATUS 4 Sheets-Sheet 4 Leonard V. Lione Inventor By WAttorney TANK WASHING APPARATUS Leonard V. Lione, Fanwood, N.J.,assignor to Butterworth System, Inc., a corporation of DelawareApplication August 5, 1957, Serial No. 676,110

5 Claims. (Cl. 239-227) The present invention relates to an apparatusparticularly adapted for cleaning the interior wall surfaces of acontainer vessel. More particularly, the invention relates to a tankwashing apparatus providing for the discharge of high pressure jetstreams of a cleaning liquid so as to impinge against the interior'wallsurfaces of such container vessel. The invention further relates to suchan apparatus wherein a nozzle structure is driven through an overridingclutch mechanism and a similar mechanism is provided in combination withsupport means for said structure. Still more specifically, the inventionrelates to a tank washing apparatus wherein the operating structure ismade up of a series of substantially self contained individual operatingunits mounted in relatively spaced relation along a common axis to forma unitary assembly, and a nozzle structure mounted on and driven throughsaid assembled units.

In conventional tank washing apparatus of the char;

acter contemplated, a nozzle structure is mounted on a verticallysuspended housing for rotation about a horizontal axis, while thehousing is rotated about a vertical axis. Conventionally, also, thehousing contains a water motor, or impeller, driving speed reductiongears for rotation of the nozzle and housing. In some devices, the gearsand other parts of the driving means are contained within the housing,while in most such devices the operating parts and gears are mountedexternally, and/or supported in bearings havinglarge clearances toprovide for lubrication and/or cooling by water or other cleaningliquids escaping therethrough. v

In the first mentioned apparatus design difiiculties are encountered inthe original manufacture and assembly of the apparatus. In order tomaintain a lubricated drive means and gear box, effective seals must beestablished, and leakage of the cleaning liquid eifectively limited.These requirements are difiicult to attain in the limited spaceavailable. They are also complicated by the fact that cleaning liquidpressures above ,150

p.s.i.g. may be attained in the fiow passages through the housing.

In the second design form, the exposed mechanisms and gearing are mostliable to damage. Also, because of the loosely fitted operating parts,at even moderate pressures leakage is so excessive that effectiveness ofthe nozzle streams is considerably reduced.

A further difficulty is experienced with conventional apparatus formswhere openings provided for introduction of the assembled device aresmall, and require precise alignment of the nozzle structure beforeintroduction and removal. In such circumstances damage may occur throughpressure exerted against reduction gear parts or otherwise. In anotherinstance, while attaching means must be provided for rigid coupling to acleaning liquid supply conduit, during attachment this means must befree to rotate with reference to the housing, and vice versa, withoutexcessive leakage under the operating pressures.

It is an object of the present invention to provide a- "ice unitswhereby to facilitate initial construction and subsequent service orrepair. In addition, it is an object of this invention to provide meanswhereby parts of the assembly required for fixed or interacting relativerelation in service may be relieved of such relationships when theassembly is not in service.

The invention and its objects may be more fully understood from thefollowing description, especially when it is read in conjunction withthe accompanying drawings, of which:

Fig. 1 is a view in elevation from the nominal front of the apparatuswith parts broken away or removed to show certain essential features ofconstruction contem plated according to the invention;

Fig. 2 is a plan view looking down on the apparatus as illustrated inFig. 1;

Fig. 3 is a view of the apparatus in longitudinal section with partsbroken away and in elevation taken generally along the line IIIIII ofFig. 2.

Fig. 4 is a view in horizontal section taken along the line IV-IV ofFig. 3, with parts shown in plan view;

Fig. 5 is an exploded view of a portion of the discharge nozzlestructure as shown in Fig. 3, taken'substantially along the line V-V ofFig. 1 and including the overriding clutch and driving means therefor;and.

In the drawings, like parts are designated by the same:

numerals. Accordingly, the several figures will be referred tospecifically by number only as required to' identify parts as shown inspecific figures.

As shown, the apparatus is composed of a series of sub-assembly unitsincluding a gear case 1, an impeller case and nozzle structure supportunit 2, a combined housing cap, support tube and coupling unit 3, and anozzle structure 4. 3 are provided so as to be joined in superposedascending order along a common axis and in spaced relationlongitudinally thereof.

The gear case unit 1, as shown, is shaped to provide vertical side wallportions 11 of substantially horseshoe shape, wherein the ends, orquarters are connected by a flat vertical cross wall portion at thefront of the case. The upper end, or top wall 13, matches the side wallperipheral conformation and is integral with such wall portions. Theupper surface of the gear case unit is stepped upwardly from the flatwall portion 12 in two steps. Primarily this is to provide a maximumspacing between it and the bottom wall portion 45 of the impeller case 2next above in the complete assembly, and

. with the cross wall 12. Thus, these bosses provide an enclosure openat the cross wall end. In addition, each Patented Dec. 15, 1959 Also asshown, the units 1, 2, and' V 3 boss terminates at its upperend in aplane common to that of said platformed boss, and further is drilled andtapped.

The top end wall 13 of the gear case 1 further provides guideand'stop'means for proper location of the unit 2 next above. In the unitas shown, the guides take the form. of two oppositely disposed smallerbosses 16 and 17 inwardly of the peripheral bosses 15. Each of thebosses 16 and 17 is shouldered to provide curvilinear, inwardly facingvertical wall portions 16a and 17a respectively. The; inner side oftheboss 14 is similarly shouldered'at 1 8, and on substantially the sameradius. The function,

depth and radial focus of the shouldered portions 16a,

' tudinal axis of the complete assembly. Bearings 2th: and

b provide rotational guides for the shaft ends. The bearing 20b,disposed-in a suitable passageway defined in the upper end wall 13 ispress fitted therein in fluid,

tight relation thereto. The upper end of the shaft is extended throughthe bearing above the. upper end wall and is rovided with a retainerseal'ZGc. The upper end of the shaft'20' also provides one part of ashaft coupling. As shown, this part is a recessed or grooved portion 20dadapted to receive a tongue provided on the lower end of another shaftsection extended from the impeller case 2. The axis of the shaft 20 isalso the focus of curvature for the shouldered portions 16a, 17a, and18.

The worm 19 engages a worm wheel 21 mounted on a shaft22 driven thereby.This shaft is mounted on suitable bearings within. the case, one ofwhich is contained in a cap 22a threadedin a receiving passagewayprovided in the case cross wall 12. The shaft 22 is at right angles tothe shaft 20, and radially spaced therefrom. The shaft 22 also carries aspur gear 23 adapted to engage a meshing gear 24 mounted on a shaft 25parallel to the shaft 22 and radially spaced from shaft 20 on theopposite side thereof from the shaft 22.

A boss 26 on the outer surface of cross wall 12 defines a passagewayadapted to receive a combined shaft seal, bearing retainer and casebearing 27 for the shaft 25 adjacent its outer end. The inner end of theshaft 25 is supported by a suitable bearing in the case wall portion.11. This end of the shaft 25 carries abevel or miter gear.

28, while the outer end extends through the element 27 to receive a spurgear pinion 29.

A fourth shaft31 is supported in a passageway 14a defined in the boss14, and by means of a bearing and retainer seal assembly 32 adapted forthreaded engagementin the passageway. The upper surface of the retainerseal is disposed substantially flush with the surface of the boss, andthe upper end of the shaft flush with retainer surface. This'end of theshaft is provided with a threaded recess 31a, adapted to receive thethreaded end ofanother shaft section as later set forth. The shaft 31isdisposed so that its axis is in right angular intersecting relation tothe axis of the shaft 25. A collar portion 31b suspends the shaft 31 onthe bearings therefor. The lower end of the shaft supportsja miter gear33 for meshed relation with the gear 28 on shaft 25. The lower end ofthe case 1 is moulded to a substantially circular contour and isprovided with a removable sealed cover plate 34.

As illustrated by Figs. 1 and 3, the impeller case is next in theascending order of the assembled units. This unit has a conformationsubstantially corresponding to that of the gear case 1, includinghorseshoe shaped side Wall portions 42, and a flat cross'wall portion43. Top and bottom end wall portions 44 and 45 respectively are formedintegrally with .the side wall and cross wall portions, and are flangedoutwardly from the side wall portions of the case as indicated bynumerals Za and 2b. The bottom end wall flange 2a is adapted to beseatedon the bosses 14 and 15 of the case and to be attached thereto .as

by the bolts shown. The upper end wall flange 2b is adapted to receiveand be bolted to the lower end of the housing cap of unit 3.

The cross wall 43 is of substantially circular, peripheral contour,extending radially beyond the side wall and bottom end wall portions 42and 45. Integral with the cross wall 43 is annular peripheral rim wall46 extending outward therefrom at right angles to the surface, and aconcentric axle tube 47, which extends outwardly beyond the rim. Betweenthem, the rim wall 445 and the axle tube 47 define an annular recesswith the obverse surface of the cross wall 43 forming the bottomthereof. In a lower sector of the cross wall 43, and displaced from adiameter thereof which is parallel to the assembly axis, the rim isthickened to provide a radial extension portion 46a. This portiondefines a chamber having a central axis lying substantially in acircular line common to the major portion of the outer periphery of therim wall 46. The chamber is of circular contour, opening through thereverse surfaceof the wall .43, and adapted to receive the outer end of.the geancase shaft 25 and the attached spur gear 29'. As shown, theextension 46a is also located so as to match the location'of the shaft25 and gear 2? and to be concentric therewith. Means are provided toseal the boss 26 in the opening through the wall 43 and'the rimextension portion 46a. The chamber, by reason of its disposition alsoopens into the recess between the wall 43 and the axle tube 47. Spidervane portions 47a in the outer end of the tube 47 support a projectingflow diffuser element 48, and a nozzle support stub shaft and bearing49.

As shown, the bottom wall 45 inclines downwardly at 45a to join thereverse surface of cross wall 43 substantially at a level correspondingwith the juncture of the lower half of the axle tube 47 with the obversesurface of cross wall'43.

The case 2, defines an interior, substantially L-shaped, passageway 41which opens at the upper end through the upper end wall portion 44 byway of an integral axial tubular portion 44a, and at the lower endthrough the cross wall 43, and the axle tube 47. Within the passageway41, and centered on the axis of the assembled structure is an upstandingannular boss 45b, integral with the bottom end wall 45, providing ashaftway which opens through thebottom wall 45. A buttress web 51connects the boss 45b with the wall portion 42.

The upper end of the tubular portion 44a is adapted to receive andrigidly retain a guide vane insert 52, wherein the vanes 53 are formedfrom a root 53a at the upper end to extend radially from a hub 52a to arim 52b, and curved downwardly to a delivery edge 53b, the root anddelivery edge each lying in a line related to the hub axis by an angleof about 45; the hub having an axis common to the case 2 and theassembled structure.

Also disposed concentric with the assembled structure is a drive shaftsection 54, the upper end of which is received'for rotation in a bushing55 mounted in the hub' 52a. The lower end of the shaft section 54extends downwardly through the boss 45b and outwardly through the bottomwall 45, terminating in a coupling part 5411 adapted to engage and matchthe coupling part 20d of the gear case drive shaft 20. As shown the part20d is a grooved end portion, while the part 54a is a tongue which fitsthe groove.

Intermediate the upper end of the boss 45b and the vaned hub 52a, avaned impeller, including a'hub 56and impeller vanes 57, is mounted onthe shaft 54, being fixed in relation to the shaft and supported thereonby a collar 54b. A bushed seal-bearing 58 for the shaft 54 is providedin upper end of the boss 45!), and expansion spring 59between thebearing 58 and collar 54b maintains the hub 56 in rotationablesurfacecontact with the bearing 55,. while-exerting pressure against theseal-bearing and bushing assembly 58. A screwdriver slot 540 is providedin the upper endof the shaft 54. The impeller vanes .57

are curved downwardly from an upper edge 57a to a lower edge 57b in adirection opposite to that of the vanes 53, and with a slightly greaterradius of curvature. The upper and lower edges of the vanes lie in aline at an angle to the hub axis which is substantially equal to theangular relationship of the vanes 53 to the hub 52a, whereby cleaningliquid is initially directed against the impeller vanes 57 by the guidevanes 53 at an optimum angle of about 90".

A portion 42a of the case side wall 42, opposite to the extensionportion 46a of the cross wall 43, is enlarged and drilled longitudinallyto form a shaftway 42b. This shaftway has an axis in right angularintersecting relation to the axis of the chamber in the extensionportion 46a, and to the axis of gear case shaft 25. A shaft 62 disposedin this shaftway extends downwardly therethrough. The lower end 62a ofthe shaft is threaded for connection in the threaded recess in the upperend of gear case shaft 31 to be driven thereby. The shaft 62 iselongated, and the upper end 62b extends upwardly be yond the shaftwayand extension portion 42a. The shaft carries a spur gear 63 at its upperend, and also is provided with a screwdriver receiving slotted portion620 therein.

Referring again to the bottom wall 45, it is to be noted that the loweror outer face is milled about the periphery common to the flangedportion 2a thereof, and along a contour substantially conforming to thatof the side Wall portions 42, whereby to produce an angular, shoulderedperipheral recessed portion 64, having an inner vertical wall depthslightly less than the shouldered portions 16a, 17a and 18 provided inthe bosses 16, 17, and 14 respectively, and a radius of curvaturesubstantially equal to that of the shouldered portions 16a, 17a and 18.With the flange 2a in contact with the upper ends of the bosses 15 and14, then the recessed wall 64 is engaged by the wall portions 16a and17a to guide the case 2 into alignment with the case 1, with bolt holesin the flange 2a aligned with those in the bosses 15 and 14, the wallportion 64 being finally engaged by the shoulder Wall 18 acting as astop therefor.

In the unit 3, the numeral 71 designates a support and cleaning liquidinlet tube having an enlarged lower end 72, internally and externallyshouldered as at 73, and at 74 and 75 respectively, and defining aninternal passageway 76c flared at its inner end to match the passageway41 at the inner periphery of the annular shoulder 73. The tube 71 issealed in rotative relation to the axial tubular portion 44a of theimpeller case top Wall 44, by means of the annular seal ring 44b mountedand disposed as shown.

In the structure illustrated, the external shouldered portions 74 and 75respectively provide mounting surfaces for an externally toothed ringgear 76, and the inner race 77 and rollers 77a of a two part conicalroller hearing. The other conical raceway portion of the bearing isindicated by the numeral 78. The ring gear 76 is retained againstlongitudinal movement on the tube 71 by means of a spring retainer ring79, and against rotation by means of a tooth portion 74a on shoulder 74,adapted to be re ceived and engaged by a recessed portion 76a in thering gear 76. The raceway 77 is press fitted upon the tube 71.

The housing cap of the unit 3 is designated by the numeral 81. This is asubstantially cup-shaped inverted cap element, having a wall portion81:; defining a passage for the upper end of the tube 71, which, asshown, is

adapted to extend through such passageway in sealed,,

. 6 of the tube 71 in rotative surface relation, and the respective wallsurface portions are sealed as by the seal ring 80. The shoulderedportion in the cap 81 is adapted to receive the conical bearing raceway78 in press fitted relation. Bosses such as indicated at 86 and 87peripherally of the rim of the inverted cup shaped housing 81 aredisposed and adapted to be received by the flange 2b in aligned relationto bolt holes therein for rigid connection of the case thereto. Thebosses such as 86and 87, extend beyond the housing rim, whereby toprovide spaced separation of the housing 81 from the flange 2b. 7

' Integral with the outer wall of the housing 81 there is formed athickened radial extension 88. This ex: tension portion is drilled on anaxis parallel to the central axis of the housing, and the assembly, toprovide a shaftway 88a to receive the upper end 62b of the shaft 62, anda chambered portion 88b at the'upper end of the shaftway. This chamberedportion opens through the inner wall of the housing into the chamberedportion 81b, and is adapted to receive the spur gear 63 on the upper endof the shaft 62. The disposition of the chamber and the dimensions ofthe ring gear 76 and spur gear 63 are such as to provide for engagementbetween the gears. A threaded cap 89 provides a closure for the upperend of the shaftway and chamber.

Included in the sub-assembly 3 is a means for coupling the apparatus toa source of cleaning liquid, such as a hose or pipe, not shown. Thismeans is composed of a color 91 and a male coupling element 92exteriorly threaded for engagement by a coupling nut on a hose or pipeconnection. The collar 91 and element 92 are joined by means such asbolts 920.

The collar 91 is freely fitted on the upper end of the tube.71, as isalso the element 92. Each of the collar 91 and element 92 is formed withan annular shouldered portion 91a and 92a disposed for opposite facingrela-' tion when assembled on the tube 71, and the coupling element 92is provided with an annular seal ring 9211 to engage'the outermost endof the tube 71. A ring portion 91b formed integrally with the collar 91and extended radially there-from provides means for attaching a ropesupport and guide means.

The face of the shoulder 91a on collar 91 is provided with a series ofnotched portions 93 forming a corresponding series of teeth 94, whereinthe tooth and notch side wall portions 95 are inclined at an angle'ofbetween about 30 and about 60 to the clearance line of the teeth. Thecollar thus forms the primary element of an overriding clutch, whereinthe secondary clutch element is an inwardly flanged annulus 96 adaptedfor threaded engagement with the upper end of the tube 71 between theshouldered portions 91a and 92a, and maintained in such engagement by aretainer ring 97. The lower edge of the annulus 96 is notched andtoothed to match the upper surface of the shoulder 91a, the notch andtooth portions being designated by the numerals 98 and 99 respectively,and the inclined side Wall portions by the numeral 100. The shoulderedportions 91a and 92a are spaced at a distance at least equal to theassembled distance between the surface of a tooth portion 99 and theupper surface of ring 97, plus the depth of a notch portion 93, wherebythe crown surfaces of tooth portions 94 and 99 may be disposedsubstantially in a common plane.

The remaining sub-assembly unit is the nozzle structure 4, and the'meansfor driving the nozzle structure for rotation about the axle tube 47.Basically, the nozzle structure 4 is composed of an annular hub 101having annular shouldered portion 102, wherein said hub is adapted fortelescopic, journalled fit over the axle tube 47. Integral with the hub101, are at least two nozzle portions 103 and 104 which, with the hub101, forms a substantially offset T discharge conduit means. A recessedportion 101a internally of the hub is adapted to be received in sealedrotative relation to the flow diffuser element 48 and to be axiallyengaged by the outer end of the stub shaft 49, through an axiallydefined passage in the hub and radially recessed portion 1010. A cap 105provides for threaded engagement with the threaded end of the shaft 49,and maintains the mounted relationship of the nozzle structure to theaxial supports therefor. Set screws 105a prevent loosening of the cap105.

A series of annular seals, including seals such as indicated by thenumerals 106 and 107 are provided against liquid leakage from or intothe related rotative joints. Also, where such seal is intended to holdagainst a positive pressure of liquid, as is the seal 106, provision ismade to release such pressure intermediate the seal and the jointprotected. Thus, in the nozzle structure 4, the face of the hub portionis provided with a series of passageways 108 defined therein so as tocommunicate with the joint between the nozzle and the axial diffuserportion 48 intermediate the seal 106 and the bearing 109. Additionally,to seal against the pressure of cleaning liquid passing into and throughthe nozzle structure 4, the axle tube 47 is provided with a pair ofannular groove portions spaced longitudinally of the tube at the outerend thereof and adapted to receive seals 110 and 111. To relieve thepressure of liquid passing the first seal 110, and to discharge any suchleakage, the hub 101 is provided with an annular groove portion 112disposed so as to lie between the seals. Radial passageways 113, alsodefined in the hub 101, communicate between the groove portion 112 andthe ambient atmosphere.

As shown in Fig. 3, when the hub 101 is mounted on the axle tube 47, theannular shouldered portion 102, with the rim 46 and cross wall 43 definean encased chamber in which the outer wall surface of the hub, portion102 is opposed to the inner wall surface of the rim 46, and the hubshoulder of the portion 102 is opposed to the cross wall 43. Also asshown in Figs. 2 and 4, the shoulder portion defines an annular recess114 paralleling, and intermediate the outer and inner wall surfaces ofthe hub. The outer edge of this recess defines a plurality ofperipherally spaced slots 115, extending through the face of theshoulder, and a plurality of passageways 116, defined in the hub 101,communicate between the bottom of the recess and the interior of thenozzle structure within the hub, and at the roots of the nozzles 103 and104.

Within the recess 114 is disposed an annular seal member 117 of aresilient, deformable material, such as an O ring of rubber or asynthetic material. Also disposed in the recess 114 toward the outer endthereof is an annular overriding clutch plate 118 provided with aplurality of ear portions 118a adapted to fit the slots 115 in the faceof shouldered portion 102, and equal in number to the number of suchslots. Each ear portion 118a is under cut to permit a portion of theplate to enter the recess below the bottom of the slots, and to provideclearance for reciprocal movement o'f the ears and plate within thedepth of the slots.

As" shown more specifically in Fig. 5, the outer face of the clutchplate 118 is provided with a series of tooth and notch portions 119 and120 respectively disposed in alternate sequence circtunferentially ofthe plate face. Each notch has a depth substantially equal to the heightof adjoining tooth portions, and the tooth wall or face connectingbetween the crown of a tooth and the bottom of a notch is angled towardthe notch center. Preferably the tooth face angle is from about 30 toabout 60 to the clearance line. The total depth of each tooth and eachnotch is preferably substantially equal to the depth of the plate undercut portion, and the total thickness of the plate, including the toothportions, is substantially equal to the depth 'o'f'thjeslots 115.

Next in sequence from the face of shoulder portion. 102 toward the innerend of the hub 101, is an annulargear 121, having peripheral gear teethmatched to the spur gear pinion 29, and adapted to be disposedforrotation on the hub while engaged by said spur gear. The outer faceof the gear 121 provides a series of'notch and tooth portions 122 and123 respectively, similar and' equal in number to those provided by theplate 118, butface of the gear, which butts against the shoulder facejportion. The gear is retained against the shoulder face, by a springsteel retainer ring 124 fitting against the face of a recessed portionon the inner side or face of the gear and engaged at its inner peripheryin an annular groove in the wall of thehub portion 102.

In assembling the apparatus according to the present invention, aparticular feature of the invention is emphasized. This feature involvesthe separability and re:

placeability of the gear reduction drive sub-assembly comprising thegear case 1.

This unit provides the first unit in the assembly-procedure, and ispreferably placed on a flat-surface, or held in a vise, with theextended end of shaft 20 and-the boss 14 uppermost. The shaft 2% is thenrotated, as by means of a screwdriver blade in the slotted portion 20d,so as to align the slot in substantially parallel relation to the axisof the shaft 25. With the shaft 20 in this position, the impeller case 2is prepared for mounting on the gear case 1 by rotating the shaft 54with means of a screwdriver blade inserted in the slot 540, so assubstantially to align the tongue 54a with the axis of the dilfuse'relement 4&5 and axle tube 47. With the shafts thus positioned, theimpeller case flange 2a is applied to the bosses 15 at the forwardportion of the side wall 11 and substantially at the ends of the gearcase cross wall 12, and slid over the remaining bosses 15 to the outerperiphery of the boss 14. During such movement, the recessed portion 64will first engage the vertical walls of the shouldered portions 16a and17a, in the bosses 16 and 17 respectively, thereby to be guided foralignment of the impeller shaft tongue 54a, with the slot 20d in theshaft 2%. When the recessed portion 64 abuts against the wall ofshoulder 18, the impeller case will be positioned with the spur gear 29in thechamber provided therefor in the portion 46a, and with theshaftway in the portion 42a substantially centered on the threaded endof the shaft 31. As thus'positioned, the flange 2a is bolted to thebosses 15 and 14.

Next, the tube '71 is applied over the tubular inlet portion 44a, theshoulder 73 engaging the rim 52b of the attached guide vane element.With the tube 71 in place, the housing cap 51 is applied over the tubeso as to align the peripheral and extended boss portions of the cap,such as designated by the numerals 86 and 37, with the correspondingbolt holes in the flange 2b of the'impeller case 2. By reason of thepredetermined location of the radial extension 3%, this part is nowlocated so as to aiign its defined shaftway 33a with the shaftway 42bdefined in the portion 42a of impeller case 2. Before mounting thehousing cap 81, of course, the seals Si? and $2 have been properlyapplied in their receiving groove portions shown, and the ring gear 76andbearing parts 77 and 73 have also been applied in the relationshipsshown and described. 7

Now the shaft 62 is inserted in the shaftway 83a, and

through that part 42b which is defined in the portion 42a of theimpeller case 42, into threaded engagement with the upper end of theshaft 31 in gear case 1. Engage merit of the shafts 62 and 31 isaccomplished by means of a screwdriver, of which the blade is-insertedin the slot portion 620. As the shaft 62 is thus engaged, theg'fiar63'becomes engaged with the-gear 76. CQntinued'rotation of the shaft 62rotates the tube 71, until the shaft is completely seated. The threadedcap 89 is then inserted to seal the chamber 88b.

The collar 91 is now slip fitted over the upper end of the tube 71 whichextends through the upper end of the housing cap 81. The annulus 96 isthen threaded on the tube with the internal annulus flange engaging ashoulder on the tube as shown, and the retainer ring 97 is applied. Aspreviously noted, with the collar 91 at rest on the upper end of the cap81, the crowns of the teeth 94 formed in the collar flange 91a should bein substantially co-planar relation to the crowns of the teeth 99 on the.lower end of the annulus 96. The male coupling 92 is now slip fittedover the end of the tube 71, and bolted to the collar 91, to completethe main part of the assembly.

- At this time, the nozzle stiucture may be prepared for mounting on theaxle tube 47. As a first step, the seals 106, 107, 110, and 111 may bepositioned in the receiving grooves therefor. Next the ring 117 isinserted in the recess 114, and the clutch plate 118 inserted over thering 117 with the ears 118a disposed in the slots 115 and teeth 119facing toward the inner end of the hub. The annular gear 121 is thenapplied, to the shouldered hub portion 102 with the teeth 122 facing theteeth 119 on plate 118, and the retainer ring 124 is fitted into thegroove provided on the wall of shouldered portion 102.

-As thus assembled, the nozzle structure 4 is prepared for mounting onthe axle tube 47. This is done by aligning the peripheral teeth on thegear 121 with the teeth on the gear 29, and sliding the hub 101 over theaxle tube 47, with the threaded end of the stub shaft 49 extendedthrough the hub axial passageway 10112. The cap 105 isthen threaded onthe shaft 49, and the set screws 105a tightened. .,-A particular featureof the apparatus provided by the unitized assembly described resides inthe arrangements whereby the operating parts required to be lubricatedardprotected from access of a cleaning liquid passed through thedischarge passageway and nozzles. As shown, each compartment of theassembly except the nozzle structure is a substantially self containedunit, and, in the assembly is substantially separated from a nextadjoining unit. Thus, with cleaning liquid employed at high pressures,the unit separation is utilized to prevent leakage from one unit fromreaching another unit directly under the operating pressure. Forexample, a vulnerable area in most machines of the type contemplated isat the juncture between'the liquid inlet and the impeller housing,another is at the juncture between the gear enclosure andthe impellerhousing and liquid flow passageway. In the apparatus according to thepresent invention each .of .these junctures are pressure relieved bydirect access to an ambient atmosphere at a lower pressure. Thus, .thefailure of the seals provided for high pressure zones does notautomatically lead to contamination or damage in all adjoining zones.,This feature is of special importance for the protection of suchelements of the structure as the bearings and gears in the housing capunit, the gear case unit, and the directly related nozzle drive.

Another particular feature of the apparatus is found in the provisionfor removal, replacement, or substitution of the drive gear sub-assemblyas a unit. This may be accomplished by first rotating the collar andcoupling 91 and 92 respectively to expose the cap 89 in extensionportion 88, and then removing the cap to provide access to the upper endof the shaft section 62. With a screwdriver blade inserted in the slot620, the shaft is unthreaded from its connection in the upper end ofshaft 31, and lifted slightly in its shaftway to clear the boss 14. Thenthe tongue 54a in the upper end of the impeller shaft 54 is aligned inright angular relation to the cross wall 43 by turning the slot 540 inshaft 54 into such alignment. Now by sliding the assembled units 2, 3and itforward over the bosses and 14, these units may be separated fromthe gear case unit 1. A new or replace ment gear case unit may beinstalled by reversing the procedure. By substituting gear case unitshaving gear trains of different ratios, the operating characteristics ofthe assembly may be altered so as to provide for a wide range ofrotational cycle rates for either or both of the nozzle structure andthe complete assembly. It is preferred, however, that while rotationalspeeds may be altered the basic ratios between the rotation rate of thenozzle structure and that of the whole assembly be retained.

An additional feature of the invention is to be found in the simplifiedforms of the clutch mechanisms provided to permit manual rotation of theassembly about its longitudinal axis and of the nozzle structure aboutits rotational axis, without dismounting parts, and Without damagingeffects upon gears, shafts and bearings included in the drivetransmission system. In the one instance the clutch arrangement is suchas to be engaged by the suspended weight of the assembly, plus thepressure of the cleaning liquid stream, in the other arrangement theclutch is engageable under the hydraulic pressure of the cleaning liquidstream as discharged from the nozzle structure.

In a typical cleaning operation, the assembly is prepared for use byconnection to the discharge end of a high pressure hose or other conduitthrough the male coupling element 92. Usually such connection will bemade with the assembly in a horizontal or vertical position, whereby theclutch teeth 94 and notches 93 of the collar 91 are disengageable fromthe notches 98 and teeth 99 of the annulus 96. With the connection made,the assembly is inserted through any suitable opening or hatchway in thetop wall of a container vessel, and preferably a hatchway disposed in,more or less concentric relation with the walls to be cleaned ortreated. This opening, because of the overriding clutch on the nozzlestructure, need be only slightly larger than the greatest horizontaldistance between the nozzle cap 105 and the toe portion of the gear caseside wall 11. Should the nozzles be extended toward the sides of theassembly, they may be rotated manually, through the nozzle structureoverriding clutch, so as to align them in substantially parallelrelation to the longitudinal axis of the assembly. Although the supplyhose or conduit usually will be sufiicient to support the weight of themachine, it is preferable to provide an auxiliary support means byattaching a rope to the collar ring 91b. This rope may also serve as ameans for guiding the machine during introduction or removal of themachine.

When inserted Within the tank and suspended therein, a cleaning ortreating liquid is supplied through the supply co-nduit connection undera pressure such as to discharge jetted streams thereof from the nozzles103 and 104. Preferably the machine is located so as to be not more thanabout twenty feet from a major portion of the container vessel interiorwall surfaces. If greater distances are involved, the machine may haveto be relocated in different areas of the vessel to accomplish propercontact of the jetted streams with all portions of the wall surfaces.Flow straightening means formed and/ or disposed in the dischargenozzles will aid in delivery of solid streams of liquid for impactagainst the wall surfaces to be contacted thereby.

The liquid flowing through the inlet tube 71 is directed against theimpeller blades 57 by means of the vanes 53, both at the inlet of thepassageway 41 defined in the impeller case 2. Thence flow passesoutwardly through the axle tube 47, and is discharged over the diffuserelement 48 through the nozzles 103 and 104. In passage through thenozzle structure 4, the pressure of the liquid flow stream is appliedthrough the passages 116 and recess 114 to the inner side of the 0 ring114a, forcing the ring toward the outer end of the recess and intoengage: ment with the clutch plate 118. Under such pressure,

aelzaaa the Q ring and plate 118 are moved toward the toothed outer faceof the gear 121, which is held against movement inwardly of the assemblyby means of the retainer ring 124. In this first engaging relationship,the teeth. and notches in the plate 118 and. gear 121 may or may notmesh.

In the meantime, however, action of the flow stream on impeller blades57 will rotate the shaft section 54 and in turn the shaft section incase 1 to actuate the gear train and shaft 25. Through shaft and spurpinion 29' and the annular gear 121 is rotated, and as the tooth andnotch portions of the plate 118, and gear 121 come into meshingrelationship, the pressure on the 0 ring 11441 forces plate 118 intomeshed engagement with the gear 121. Rotation of the plate by engagementwith the gear is transmitted to the nozzle structure through the earsand slots 118a and 115 respectively. So long as pressure is applied tothe 0 ring the gear will be main-.- tained in locked driving relation tothe nozzle hub. When the liquid pressure on the O ring 114a is relieved,the clutch plate and gear faces do not disengage automatically, but whenthe nozzle is rotated manually, the plate 118 will be forced into therecess as the teeth 119 ride over the angled wall portions of the teeth123, along with the O ring 114a.

Actuation of the gear train and the shaft 25 also will actuate the shaftsection 31, and through it the shaft section 62. As previouslydescribed, the gear 76 is fixed in relation to the tube 71 by the toothand recess portions 74a and 76a respectively. Also, the tube 71 isrigidly fixed by the weight of the assembly and the water pressure tothe coupling 92 through the overriding clutch arrangement, the toothedcollar and annulus members, and through the coupling to the connectedsupply conduit means. Rotation of the shaft 62 and the attached gear 63,therefore, causes the gear 63 to walk around the fixed gear 76 as asatellite while drawing the assembled portions including cases 1 and 2,and housing cap 81 along, with consequent rotation of the assembly aboutthe tube 71 and the longitudinal axis. In the meantime, of course, thenozzle structure is rotated about the axle hub.

Each of the spur pinions 28 and 29 being driven through the same shaft25, and at the same speed, if bothv gears 76 and 121 had the same numberof teeth, nozzle and assembly would rotate at the same rate, and thepaths of the nozzle discharge streams would be constant and would track.The object, however, is to provide .constantly changing stream pathswithin the limits of eflicient operation. It has been found that with aliquid pressure of between about 150 to about 200 pounds, sufficientimpact force is obtained at a distance of about twenty feet to produceeffective scouring dispersion of the streams, at the impact surface, andto obtain effective cleaning action, if the stream paths are separatedby about one foot. This result is obtainable in sixty-three revolutionsof the entire assembly if the gear 76 has sixty-four teeth and the gear121 has sixty-three teeth.

With such a proportional relationship, for each revolution of thecomplete assembly about the longitudinal axis, the nozzle will makeabout 1.0158 revolutions about,

the radial axis provided by the axle tube 47. In other words, for everycompleted revolution of the assembly about the sixty-four tooth gear 76,the nozzle will make one revolution about the tube 47, plus a distanceequivalent to one more tooth, since the gear 121 has only sixtythreeteeth. The difference as noted above is .0158 revolution, or 5.71(360+63) in the 360 periphery of each of the gears 76 and 121.

With the axis of the nozzle considered to be located in a horizontalplane the axis of each stream will describe a curved path the tangent.of which is 45 in relation to such plane, and will advance about 5 .7lalong a circle in the stated reference plane, in each revolution of theassembly. With two nozzles as shown, the respective paths will beseparated by 2.855". Also, inasmuch as two nozzles are employed, in anyseries of successive travel paths, one will be in a downward directionand one in an upward direction. All paths in the same direction will beparallel, and with those extending generally upward intersecting thoseextending generally downward substantially to form a criss-cross orcheckerboard pattern over any given wall surface.

The path relationships preferred have been stated, others may beattained by varying thehunting tooth ratio, i.e., a tooth relationshipof 62 to 64 between the nozzle and assembly gears 121 and 76respectively would result in a different degree advance of eachpath,namely 5.8064" (360+62). If the ratio were 65 teeth in the nozzle gearto 64 in the assembly gear, the advance would be 5.6923. After onecycle, or a number of revolutions about the longitudinal axis of theassembly which is equal to the number of teeth in the nozzle gear 121,the paths repeat themselves. As may be noted, the degree of advancedecreases With an increase in the number of teeth in the nozzle gear121, and the number of paths described increases.

The rate at which the cycle is accomplished depends entirely upon thereduction accomplished by the gear train within the gear case 1. In apreferred system as shown, the ratio between the Worm 19 and the wheel21 is 40:1, and between the pinion 23 and spur gear 24 it is 53:12. Theratios between the gears 121 and 76, and the pinions 29 and 63 are 63:10and 64:10 respectively. Where intensive contact action is required, thereduction is increased and thereby the speed of rotation is reduced,enabling the streams to pass over the wall surfaces more slowly. In asimilar instance, if the number of teeth the nozzle gear 121 isincreased separation of the successive paths over the surface would bereduced. Ordinarily, the ratio between nozzle gear 121 and assembly gear'76 is preferred to be 63:64. More intensive or less intensive contactis attained by varying the speed, or gear reduction ratios in thecase 1. To accomplish such speed variations, any one of a series of geartrains may be substituted by substituting units containing such preselected trains in the manner previously described. 'If more than twonozzles are employed in the nozzle structure, the pattern described willnot change substantially, but the forming paths will be closer together.

In the alternate apparatus form illustrated by Fig. 6, an overridingclutch mechanism, substantially corresponding to that disposed at theupper end of the tube 71 in Fig. '3, is contained internally of thehousing cap portion of the unit 3 of the complete assembly. The parts ofthe alternate construction form corresponding to similar parts in theother drawings are designated by similar numerals, but in the series.

The numeral 171 then designates a support tube having a shoulder 174 onwhich have been formed a series of circumferentially spaced upstandingtooth elements 194 with notch portions between the teeth. A ring gear176, adapted for engagement with a drive pinion 163, is disposed overthe tube 171. The lower face of the gear 176 is also provided with toothand notch portions adapted to match those in the face of shoulder 174.The numeral 199 designates one such tooth. Except when the tooth andnotch portions of the gear are engaged with similar portions in the tubeshoulder face, the gear and tube are rotatable with reference to oneanother.

Also mounted on the tube 171 is one part of a roller bearing, which partincludes a raceway 177 and rollers 177a. The raceway is disposed forrelatively free reciprocal movement on the tube. A housing cap 181 fitsover the tube 171 as shown, and contains theother raceway 178 of theroller bearing assembly.

The outer or upper end of tube 171, which extends beyond the cap 181 isadapted for fixed threaded en,- gagement by a male coupling element 192.A set screw 192a holds the element against rotation after assem- 1 bly.The lower end of the coupling 192 is disposed so that the tube shall befree to move reciprocally with respect to the cap 181 for adistance atleast equal to the least height of either series of teeth 194 or 199.

In use, when the tube is relieved of the weight of the assembly it willtend to move downwardly through the housing cap 181. In this condition,rotation of the tube 171 or gear 176, one relative to the other willcause the gear teeth 199 to ride over the tube shoulder teeth 194. Whenthe assembly welght and water pressure is transmitted to the tube 171,the gear 176 will be forced against the bearing raceway 177, and theraceway in turn against a shoulder 171a in the tube 171. In thisposition the teeth 194 will be unable to override the teeth 199, andtherefore, the gear will be rigidly related to the tube, wherebyrotation of the pinion 163 will causethe rest of the assembly to berotated about the tube.

What is claimed is:

1. In apparatus of the character described, including a support tubedefining a liquid conduit having inner and outer ends, a housingassembly supported coaxially from said tube inner end for rotation aboutsaid tube axis in substantially fluid tight relation to said tube,wherein said housing assembly includes an impellercase defining a liquidpassageway opening from said tube subport at one end through an annularsupport axle extended radially from said case at the other end, and anozzle structure mounted on said axle in rotatable coaxial relationthereto, a means for rotating said nozzle structure about its axiscomprising a hub on said nozzle structure adapted for telescopicrotatable engagement on said axle, a shouldered portion on said hubdefining a radial face and a circular longitudinal wall at right anglesto said face, an annular gear mounted and retained on said shoulderwall, freely rotatable thereon, said gear having an inner face disposedin opposed relation to said shoulder face, a plurality of tooth andnotch portions on said gear inner face, an annular recess defined insaid shoulder face, a plurality of passageways defined in said hub toextend and communicate between said recess and the interior of saidnozzle structure, a resilient deformable seal ring fitted in saidshoulder face recess for reciprocally displaced movement therein, anannular clutch plate mounted for reciprocal movement on said hubshoulder wall and intermediate said seal and said gear, said plateengageable therebetween, said plate having an outer face disposed inopposed'relation to said inner gear face, a plurality of tooth and notchportions on said plate outer face adapted to mesh with those on saidgear inner face, and means to retain said clutch plate against rotationon said hub shoulder wall.

2. An apparatus for applying liquid streams to the interior wallsurfaces of a container vessel, comprising in combination a suspensionand support tube having inner and outer ends, coupling means at theouter end of said tube mounted for rigid attachment of said tube to a'liquid supply conduit, an enlarged portion at the inner end of saidtube forming interiorly and exteriorly disposed shoulders respectivelyfacing toward said inner and outer tube ends,'a first ring gear mountedon said exterior shoulder, in fixed relation thereto, a housingrotatably mounted on said tube comprising an annular housing capconcentric with said tube and disposed for rotative support thereby influid-tight relation thereto, an impeller case supported by said cap independent spaced relation thereto, said case including a top walldefining an upstanding tubular conduit portion adapted to engage saidtube within the enlarged lower end thereof for fluid tight rotativerelation thereto, front wall and bottom wall portions integral with saidcase, a tubular nozzle axle mounted on said front wall and disposed inright angular relation to the axis of said tube,.a passagethrough saidaxle, an impeller shaft and impeller mount-- ed in said passageway inaxial relation to said tube, said shaft extending through the bottomwall of said case, a nozzle structure having a hub mounted on said axlefor rotation thereon, overriding clutch means mounted on said hub, saidmeans including a second ring gear rotatable on said hub, hydraulicmeans mounted on said hub to engage said clutch means between said gearand nozzle hub, a gear case sub-assembly unit, having top, front andside wall portions, said gear case top wall portion being separablyattached to said impeller case bottom wall in axially spaced dependentrelation thereto, a drive shaft extending from said gear case anddisposed for relation axially to said impeller shaft including separableconnective means therebetween, a separable drive connection between saidgear case and said first ring gear, and a separable drive connectionbetween said gear case and said second ring gear.

3. An apparatus according to claim 2 wherein said coupling meanscomprises an annulus retained in fixed threaded engagement on said tube,said annulus having a toothed lower end, wherein said teeth includeangularly inclined side wall portions, an annular coupling element andcollar combination enclosing said annulus, said collar having aninwardly flanged shouldered portion toothed about its upper. surface inmatching relation to the lower toothed end of said annulus, said collarand coupling combination disposed for reciprocal movement longitudinallyof said tube for a distance at least equal to the distance between theroot and face of one said tooth portion.

4. In an apparatus of the character described, including a support tubedefining a liquid conduit having inner and outer ends, an enlargedportion at the inner end of said tube forming. exteriorly disposedannular shoulders facing toward said tube outer end, and a housingassembly supported coaxially from said tube shoulders by means of anannular cap fitted to said tube in telescopic, substantially fluid tightrelation, for rotation about said tube axis and for limited reciprocalmovement longitudinally thereof, saidcap and tube defining a sealedchamber including said tube shoulders as wall portions thereof; a meansfor rotating said assembly about said tube comprising a ring geardisposed in said chamber, encompassing said tube, said gear having alower face opposed to one said tube shoulder, a circumferentialmatching'series of tooth and notch portions on each said shoulder andsaid ring gear lower face engaged and disengaged by reciprocal movementof said assembly relative to said tube; a shaft way defined in saidassembly in axially parallel relation to said tube; a drive shaft insaid shaftway, and a pinion gear carried by said shaft for meshedrelation with said ring gear.

5. An apparatus according to claim 1, wherein said means to retain saidclutch portion against rotation on said hub shoulder wall comprises aseries of slots defined in said shoulder face in circumferentiallyspaced relation radially of said face, and a corresponding series ofradial ear portions on'said clutch plate, adapted for engagement in saidslots, said ear portions having a thickness less than the depth of saidslots and said plate having a thickness substantially equal thereto.

References Cited in the file of this patent UNITED STATES PATENTS

